KR100903060B1 - Shaft support structure of a swash plate type compressor - Google Patents

Abstract

The present invention relates to a shaft support structure of a swash plate type compressor in which unnecessary frictional resistance is not generated when the shaft is rotated by installing a thrust bearing supporting the shaft and a coil spring, and providing a center bore to support one end of the shaft. In the variable displacement swash plate type compressor having a cylinder block is formed, it is located in the center bore in contact with one end of the shaft when the compressor is stopped, to maintain a gap with the shaft when the shaft rotates normally Since the back race is installed, it basically blocks the frictional resistance generated when the shaft rotates to block the frictional heat, vibration and noise, as well as improve the driving ability of the shaft, as well as the thrust bearing and the coil spring. The process of producing and installing There is an effect that a reduction and simplification of the assembly process the product cost of the parts can decrease in accumulation.

Swash plate compressor, shaft, back race,

Description

SHAFT SUPPORT STRUCTURE OF A SWASH PLATE TYPE COMPRESSOR}

The present invention relates to a shaft support structure of a swash plate type compressor, and more particularly, to a shaft support structure of a swash plate type compressor in which an unnecessary friction resistance is not generated when the shaft is rotated by installing a thrust bearing supporting the shaft and a coil spring. will be.

In general, a compressor constituting an air conditioner for a vehicle is a device that selectively receives power of an engine delivered through a pulley by an intermittent action of an electronic clutch, inhales refrigerant from an evaporator, and discharges the refrigerant into a condenser.

There are various types of such compressors according to the compression structure, and generally, the compressor is divided into reciprocating type and rotary type according to the compression method and structure. Reciprocating is divided into crank, swash plate, and wobble plate, and rotary is divided into main rotary type and scroll type. Some of these compressors have a variable capacity type that can change the compression volume.

In the swash plate type compressor, a disk in which a disk-shaped swash plate installed inclined to a shaft receiving an engine power is rotated by a shaft, and by the rotation of the swash plate, a plurality of pistons installed through a shoe along the circumference of the swash plate are formed in a cylinder block. The linear reciprocating motion in the bore allows the refrigerant to be sucked / compressed and discharged.

The variable displacement swash plate compressor is configured such that the inclination angle of the swash plate installed on the shaft varies according to the heat load. Accordingly, the refrigerant discharge amount is variably adjusted while the reciprocating feed amount of the piston is changed.

As an example of the variable displacement swash plate type compressor as described above, the configuration of Korean Patent No. 748140 (hereinafter, referred to as 'prior art') will be described with reference to FIG. 1.

As shown in FIG. 1, the variable displacement swash plate compressor 1 has a cylinder block 2 having a center bore 4 and a plurality of cylinder bore 6 radially formed therein. Both sides of the cylinder block 2 are sealed by the front housing 8 and the rear housing 10. An airtight crank seal 12 is provided between the cylinder block 2 and the front housing 8, and a valve plate 14 is interposed between the rear end of the cylinder block 2 and the rear housing 10. In the rear housing 10, an outlet and an inlet for inlet and outlet of refrigerant gas, a suction chamber 16, and a discharge chamber 18 are respectively formed. The suction chamber 16 and the discharge chamber 18 communicate with the respective cylinder bores 6 and the refrigerant through the suction and discharge valve mechanisms, respectively. The shaft 20 is disposed at the center so as to extend through the front housing 8 to the cylinder block 2 and is also rotatable by the radial bearing 22 mounted to the front housing 8 and the cylinder block 2. One end of the shaft 20 inserted into the cylinder bore 6 is axially supported by the supporting means to prevent axial flow of the shaft 20. The cylinder block 2 and the front and rear housings 8 and 10 are coupled as the through bolts 24. In the crank chamber 12, a rotor 26 is rotatably mounted to the shaft 20 together with the shaft 20, and the rotor 26 also rotates together with the shaft 20. It is fixedly mounted to the shaft 20 across 12. The swash plate 28 is rotatably supported on the shaft 20, and a spherical sleeve may be interposed between the shaft 20 and the swash plate 28, in which case the swash plate 28 is It is rotatably supported on the outer support surface of the spherical sleeve. In FIG. 1, the swash plate 28 is in the position of the maximum inclination angle, wherein the spring 30 is in the maximum compressed state, and the stop surface 32a of the protrusion 32 contacts the rotating body 26. Therefore, the inclination angle of the swash plate 28 is limited by the rotating body 26. In addition, the shaft 20 is provided with a stopper 34 to limit the minimum inclination angle of the swash plate 28.

Then, the swash plate 28 and the rotating body 26 are connected by the hinge mechanism to rotate together. That is, the support arm 36 protrudes outwardly along an axis from one side of the rotating body 26, and the arm 38 extends from one surface of the swash plate 34 toward the supporting arm 36 of the rotating body 26. It protrudes. Support arm 36 and arm 38 are connected to each other by pin 40.

The pistons 42 are slidably arranged in the respective cylinder bores 6, and each piston 42 has a body 44 and a bridge portion 46 slidably arranged in the cylinder bores 6. A recess 48 is formed in the bridge portion 46 of the piston 42, and the outer circumferential portion of the swash plate 28 is positioned in the recess 48. The hemispherical shoes 50 are disposed in a shoe pocket 52 formed in the bridge portion 46 of the piston 42 to slidably engage with both sides of the outer circumferential portion of the swash plate 28. Accordingly, as the shaft 20 rotates, the swash plate 28 also rotates, and the rotational movement of the swash plate 28 is converted into the reciprocating motion of the piston 42 through the shoes 50. A cutout portion 54 is formed at one end of the piston 42, which is the surface of the swash plate 28 and the piston 42 when the piston 42 is located at the bottom dead center. The torso 44 is to prevent the contact with each other.

Subsequently, referring to FIG. 2, in the configuration of the support means for supporting the shaft in the axial direction, the support means 56 is located in the center bore 4 of the cylinder block 2 and at one end of the shaft 20. Drive race 80 coupled to one side of the thrust bearing 58 is coupled to rotate together with the shaft 20, and closely coupled to the other side of the thrust bearing 58 to the rotation of the shaft 20 It has a fixed race 82 to remain fixed regardless. It also has a coil spring 64 which eventually supports the shaft 20 by supporting the two races 80, 82 including the thrust bearing 58 in the axial direction.

However, the variable displacement swash plate compressor according to the prior art is rotated while the shaft 20 is moved toward the front housing 8 in response to the gas force in the normal operation, the coil spring disposed on the rear housing 10 ( 64, the thrust bearing 58 and the race 80, 82 are always in contact with the rotating shaft 20 to generate a frictional resistance. Because of this, the friction between the two parts caused by the heat generated wear and high heat, there was a problem to deteriorate the performance of the entire compressor.

In addition, since the thrust bearing 58 and the coil spring 64 for supporting the shaft 20 are used, not only the manufacturing cost increases but also the thrust bearing 58 and the thrust on the shaft 20. There was an inconvenience in that the driving race 80 and the fixed race 82 and the coil spring 64 disposed on both sides of the bearing 58 must be sequentially coupled.

The present invention has been made to solve the above problems, an object of the present invention to provide a shaft support structure of the swash plate type compressor which can fundamentally block the frictional resistance generated from the support structure during normal operation of the shaft.

In addition, another object of the present invention to reduce the production cost by eliminating the production of the thrust bearing and coil spring produced separately, and to provide a shaft support structure of the swash plate compressor that can improve the workability and productivity at the same time by simplifying the assembly process It is.

In order to achieve the above object, the shaft support structure of the swash plate compressor according to the present invention, in the variable displacement swash plate compressor having a cylinder block formed with a center bore to support one end of the shaft, the compressor stop Located in the center bore in contact with one end of the shaft when the shaft is, characterized in that the back race is installed to maintain a gap with the shaft when the shaft rotates normally.

In particular, the back race is characterized in that the plate shape.

In addition, the back race is manufactured in various thicknesses, characterized in that the selective assembly in consideration of the overall tolerance of the swash plate type compressor.

In addition, the back race is characterized in that it is made of a soft dust-proof material.

Further, the back race is characterized in that the through-hole is formed in the center.

In addition, the gap between the shaft and the back race is characterized in that it is set smaller than the top clearance of the compressor.

And, the gap between the shaft and the back race is characterized in that 0.05 ~ 0.35mm.

According to the present invention having the configuration as described above, by blocking the friction resistance generated when the shaft is rotated by installing the back lace to block the frictional heat and vibration and noise at the same time, it is possible to improve the driving ability of the shaft In addition, the process of producing and installing the thrust bearing and the coil spring can be omitted, thereby reducing the product cost and simplifying the assembly process by reducing the number of parts of the entire compressor.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to FIGS. 3 to 6.

3 to 6 is a view showing a shaft support structure of the swash plate compressor according to the present invention.

In addition, for convenience of description, the same reference numerals are given to the same components as those in the prior art, and detailed descriptions thereof will be omitted, and only different configurations will be described.

As shown in FIG. 3, the shaft support structure of the swash plate compressor according to the present invention includes a cylinder block 2 formed with a shaft 20 and a center bore 4 so as to support one end of the shaft 20. ), The center bore (4) is provided with a back race 100 for supporting the shaft (20).

That is, the center bore 4 is not provided with a thrust bearing 58 and a coil spring 64 to support one end of the shaft 20, but is supported by the back race 100.

In particular, with reference to FIG. 4, the back race 100 which is a characteristic component of the present invention will be described.

The back race 100 is made of a metal or alloy steel in the shape of a plate with a through hole 110 formed in the center thereof.

The back race 100 is preferably processed so that the surface in contact with the shaft 20 is smooth. This is to minimize the frictional resistance between the two components when the shaft 20 is rotated according to the normal driving of the vehicle while the shaft 20 is supported by the back race 100.

On the other hand, Figure 5 shows another embodiment of the back race 100 ', in order to reduce the shock vibration and impact noise generated in the process of stopping the drive shaft 20 driving a predetermined gap (L). A back lace 100 'composed of soft, dustproof material (rubber, silicone, cork, etc.) is adopted.

The back race 100 according to the present invention is located in the center bore 4 in contact with one end of the shaft 20 when the compressor is stopped or operated, and during normal rotation of the shaft 20. It maintains a predetermined gap (L) from the end of the shaft 20 serves to essentially block the frictional resistance between the two parts.

In addition, the back race 100 has a size corresponding to the end of the shaft 20, it is manufactured in a form that can be installed in the center bore (4) of the cylinder block (2).

In particular, the back race 100 is preferably manufactured in various thicknesses to be selectively assembled in consideration of the dimensional tolerance range between the shaft 20 and the cylinder block (2).

Specifically, as shown in Figures 3 to 6, in the machining step of forming the center bore 4 of the shaft 20 and the cylinder block 2, each of the dimensional tolerances within the error range occurs, Assembly tolerances also occur in assembling parts. Accordingly, when the shaft 20 is stopped, the shaft 20 is in contact with and supported by the shaft 20 (see FIG. 6), and when the shaft 20 is rotated, a predetermined gap L is maintained from the end of the shaft 20. By manufacturing the back race 100 to a variety of thicknesses so that the frictional resistance does not occur, it is possible to selectively assemble the compressor tolerance generated during assembly.

Here, the predetermined gap L is maintained in a narrower state than the top clearance CT of the piston 42. Typically, the top clearance CT of the piston 42 is maintained at about 0.1 to 0.4 mm from the valve plate 14 and the suction chamber 16 (see FIG. 3).

Therefore, the predetermined gap between the shaft 20 and the back race 100 is to be installed within 0.05 ~ 0.35mm.

That is, even when the shaft 20 moves toward the back race 100 and is closely supported when the shaft 20 is stopped, the piston 42 does not come into close contact with the valve plate 14 and the suction chamber 16. .

In addition, in the case of the cylinder block 2 and the center bore 4 in which the back race 100 is installed, it is not necessary to provide a space for installing the thrust bearing 58 and the coil spring 64, so that steel materials are processed more efficiently. can do.

1 is a cross-sectional view showing the configuration of a variable displacement swash plate compressor of the prior art.

FIG. 2 is an enlarged cross-sectional view illustrating a structure for supporting the shaft of FIG. 1.

3 is a cross-sectional view showing the shaft support structure of the swash plate compressor according to the present invention.

4 is a cross-sectional view showing a state diagram that operates while the gap between the shaft and the back race of FIG. 3 is maintained.

5 is a cross-sectional view showing another embodiment of the material of the back lace of FIG.

6 is a cross-sectional view showing a structure supported by the back race when the shaft of FIG. 3 stops.

<Explanation of symbols for the main parts of the drawings>

100, 100 ': Back race 110: Through hole

Claims (7)

delete delete In a variable displacement swash plate compressor having a cylinder block having a center bore to support one end of a shaft, A back race positioned in the center bore in contact with one end of the shaft when the compressor is stopped and maintaining a gap with the shaft when the shaft rotates normally; The back race has a plate shape, but the shaft support structure of the swash plate compressor characterized in that it is manufactured in various thicknesses and selectively assembled in consideration of the overall tolerance of the swash plate compressor. In a variable displacement swash plate compressor having a cylinder block having a center bore to support one end of a shaft, A back race positioned in the center bore in contact with one end of the shaft when the compressor is stopped and maintaining a gap with the shaft when the shaft rotates normally; The shaft support structure of the swash plate type compressor, characterized in that the back race is made of a soft dust-proof material. The method of claim 3, The back race shaft support structure of the swash plate compressor, characterized in that the through-hole is formed in the center. In a variable displacement swash plate compressor having a cylinder block having a center bore to support one end of a shaft, A back race positioned in the center bore in contact with one end of the shaft when the compressor is stopped and maintaining a gap with the shaft when the shaft rotates normally; The shaft support structure of the swash plate type compressor, characterized in that the gap between the shaft and the back race is set smaller than the top clearance of the compressor. The method of claim 6, The shaft support structure of the swash plate type compressor, characterized in that the gap between the shaft and the back race is 0.05 ~ 0.35mm.

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